CN103307156A - Double-toothed-surface forced braking and load-limitation coupling - Google Patents
Double-toothed-surface forced braking and load-limitation coupling Download PDFInfo
- Publication number
- CN103307156A CN103307156A CN2012100707070A CN201210070707A CN103307156A CN 103307156 A CN103307156 A CN 103307156A CN 2012100707070 A CN2012100707070 A CN 2012100707070A CN 201210070707 A CN201210070707 A CN 201210070707A CN 103307156 A CN103307156 A CN 103307156A
- Authority
- CN
- China
- Prior art keywords
- coupling
- lever
- afterburning
- ring
- braking
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Images
Abstract
The invention relates to a double-toothed-surface forced braking and load-limitation coupling, which comprises an upper end cover assembly, a spring seat, a baffle ring for a shaft, a bearing, a baffle ring for a hole, a driving coupling, a large support, a forced lever assembly, a lever forced ring, a plane bearing, a braking ring, a friction sheet support assembly and a lower end cover assembly. The coupling is characterized in that the upper end cover assembly, the spring seat, the baffle ring of the shaft, the bearing, the baffle ring for the hole, the driving coupling, the large support, the forced lever assembly, the lever forced ring, the plane bearing, the braking ring, the friction sheet support assembly and the lower end cover assembly are sequentially connected in series along the axial line direction of the large support. According to the driving coupling and a driven coupling, the engagement of inner layer toothed surfaces is adopted to carry out transmission and braking unlocking; outer layer spiral toothed surfaces of the driving coupling and the driven coupling are isolated, and overload protection is provided for a working machine; and when the machine stops, the spring seat is used for propelling the forced lever assembly to pressurize the friction sheet support assembly, so that a forced braking torque is generated, and braking is realized.
Description
Technical field
The present invention relates to a kind of bidentate face thrust type braking load-limiting coupler.
Background technique
Existing braking load-limiting coupler has the function of coupling, load limiter and break; can reach the driven off by shaft effect of connection; when machine can be protected machine when overloading; also can brake because of stopping of machine at once; but braking moment is little; and power loss is very large when work; in the situation that load is little; braking is difficult for removing; cause the whole heating of braking load-limiting coupler, therefore existing braking load-limiting coupler can not the very large braking moment of to meet the need and the working environment of high mechanical efficiency.
Summary of the invention
Purpose of the present invention: design a kind of existing shaft coupling and limit for tonnage function, very large braking moment is arranged again, the braking load-limiting coupler that machinery driving efficiency is high, and in the situation that load is very little, braking is easy to remove, and remedies the deficiency of existing braking load-limiting coupler.
The technical solution adopted for the present invention to solve the technical problems is:
Upper end cap assembly parts, spring seat, shaft block ring, bearing, hole back-up ring, active coupling, large support, afterburning lever combination part, the afterburning ring of lever, plane bearing, brake hoop, friction plate assembly and lower end cap assembly parts are along direction of axis line successively coupled in series.
Locking nut is fixed on the upper end cap by locked spacer, afterburning ring is close to locked spacer, stressed fulcrum as afterburning pivot pin, the energy band flexible spring seat that stores during the brake spring compression moves to the friction disc support direction vertically, the conical surface on the spring seat promotes to be installed in the miniature bearing on the afterburning lever, make the lever reinforcing press the afterburning ring of lever pressure is passed to friction plate assembly and driven coupling brake disc by plane bearing and brake hoop, produce large braking moment.
Driven coupling is the coupling that is fixed on the driven shaft, initiatively coupling is installed on the driving shaft by spline and (refers generally to motor shaft), friction disc support is stuck on the large support, a certain amount of displacement is arranged vertically, can not produce angular displacement, the friction disc support two sides is glued to the friction disc support two sides by the mode that gummed connects, and is installed in vertically between brake hoop and the driven coupling brake disc.
Initiatively coupling and driven coupling be owing to adopting the helical tooth flank of two-layer different helix angles, the helix angle of internal layer helical tooth flank large (starting helicoid) wherein, the helix angle of outer helical tooth flank less (working screw face).When machine start, initiatively coupling and driven coupling internal layer starting helicoid meshes at first, because the helix angle of starting helicoid is larger, the axial force that produces after the engagement is larger, when the axial force that produces has exceeded the axial pressure of brake spring, initiatively coupling moves axially to the rear of the flank of tooth, the band flexible spring seat moves together afterwards, eliminated and added the pressure that is pressed on the friction plate, removed braking, active coupling and driven coupling starting this moment helicoid has been thrown off, the working screw face begins engagement, initiatively the axial force of the working screw face of coupling and driven coupling generation and the axial force balance of brake spring reach the function that is easy to brake off and shaft coupling.During overload; broken the balance with brake spring pressure; in order to reach the balance with brake spring pressure; initiatively coupling only has vertically to the further compression brake spring in active coupling rear; until the outer helical tooth flank of active coupling and driven coupling is thrown off fully, played the effect of overload protection working machine.When the active coupling runs out of steam, the energy that stores when brake spring is compressed discharges immediately, when the braking conical surface by spring seat promotes the afterburning ring of lever, plane bearing, brake hoop and friction plate assembly and produces friction, friction plate assembly and driven coupling brake disc produce friction, have realized braking.
Upper end cap or lower end cap adopt and are bolted on the frame of working machine, upper end cap and lower end cap adopt Bolt Connection large support two ends.
The sliding bearing sleeve cylindrical adopts the mode of interference fit to connect with the upper end cap endoporus, branched afterburning pivot pin distributes equably and is inserted in the upper end cap axis hole, and one-tenth slip cooperating relationship, put respectively an identical brake spring on every forcing shaft, afterburning ring withstands branched forcing shaft, the spring adjusting nut is spun in the upper end cap screw thread, after adjusting is finished, and locking with the locked spacer locking.
The lever pivot pin is fixed on lever on the large support.
The lever reinforcing is to utilize the conical surface of spring seat to promote lever to push down the afterburning ring of lever along the swing of lever pivot pin, and move to the friction plate assembly direction vertically, successively power is passed to plane bearing, brake hoop, friction plate, friction disc support, friction plate and driven coupling brake disc, afterburning size is relevant with lever ratio.
The invention has the beneficial effects as follows; the function that not only possesses coupling; has again simultaneously the function of break and load limiter; played to shut down and braked immediately and Protection machine effect when transshipping; in the situation that load is very little; be easy to brake off, and strengthened braking moment and improved machinery driving efficiency.
Below in conjunction with Figure of description the present invention is described in detail.
Description of drawings
Accompanying drawing 1: thrust type braking load-limiting coupler profile schematic diagram.
Accompanying drawing 2: thrust type braking load-limiting coupler overall structure figure.
Accompanying drawing 3: brake hoop and active coupling assembly relation schematic diagram in the thrust type braking load-limiting coupler.
Accompanying drawing 4: the thrust type braking large support of load-limiting coupler and afterburning lever combination part schematic diagram.
Accompanying drawing 5: friction plate assembly schematic diagram.
Accompanying drawing 6: thrust type braking load-limiting coupler upper end cap assembly parts.
Accompanying drawing 7: thrust type braking load-limiting coupler lower end cap assembly parts.
Accompanying drawing 8: the afterburning lever combination part of thrust type braking load-limiting coupler.
Accompanying drawing 9: spring seat structure schematic diagram.
Accompanying drawing 10: thrust type braking load-limiting coupler brake hoop, friction plate and driven coupling position relationship schematic diagram when shutting down braking state.
Accompanying drawing 11: thrust type braking load-limiting coupler brake hoop, friction plate and driven coupling position relationship schematic diagram when starting and working state.
Accompanying drawing 12: relative position relation intention when brake hoop is with the work of active coupling in the thrust type braking load-limiting coupler.
Accompanying drawing 13: relative position relation intention when brake hoop is shut down braking with the active coupling in the thrust type braking load-limiting coupler.
Accompanying drawing 14: driven coupling shape assumption diagram.
Accompanying drawing 15: active coupling shape assumption diagram.
Accompanying drawing 16: initiatively coupling and driven coupling are in working state engagement situation schematic diagram.
Accompanying drawing 17: initiatively coupling and driven coupling are in starting state engagement situation schematic diagram.
Accompanying drawing 18: initiatively coupling and driven coupling exchange to working screw face schematic diagram from the starting helicoid.
Accompanying drawing 19: initiatively coupling and driven coupling are in static braking state profile of tooth mesh schematic representation.
In the accompanying drawing: 1-lower end cap, 2-bolt A, 3-spring washer B, the large support of 4-, 5-lever pivot pin, the afterburning lever of 6-, 7-miniature bearing, 8-bearing pivot pin, 9-bolt B, 10-spring washer B, the afterburning ring of 11-, 12-spring adjusting nut, 13-upper end cap, 14-is coupling initiatively, 15-shaft block ring, 16-bearing, the 17-sliding bearing sleeve, 18-spring seat, 19-locked spacer, the afterburning pivot pin of 20-, 21-circlip for hole, 22-brake spring, the afterburning ring of 23-lever, 24-plane bearing one, 25-brake hoop, the 26-friction disc support, 27-friction plate, the driven coupling of 28-, 29-plane bearing two, 30-rolling bearing, 31-shaft block ring.
Embodiment
Shown in the Figure of description 2: upper end cap 13 is fixed on the large support 4 by bolt B 9 and spring pad B10, and lower end cap 1 is fixed on the large support 4 by bolt A2 and spring pad A3.
Shown in Figure of description 2 and the Figure of description 6: sliding bearing sleeve 17 adopts the mode of interference fit to connect with upper end cap 13, branched afterburning pivot pin 20 is through on the supporting hole of upper end cap 13, and the connecting mode that becomes to be slidingly matched, afterburning ring 11 is enclosed within on the upper end cap 13, and withstand on the branched afterburning pivot pin 20, spring adjusting nut 12 is regulated axial position along the outside thread on the upper end cap 13, after mixing up, and with locked spacer 19 lockings, prevent angular displacement and axial displacement.
Shown in the Figure of description 2: spring seat 18 is positioned at initiatively on the coupling 14 with back-up ring 21 by shaft block ring A15, rolling bearing 16 and hole, and 22 one-tenth of branched brake springs are arranged in parallel, and a side pressure is lived spring seat 18, and the other end withstands afterburning pivot pin 20.
Shown in Figure of description 2, accompanying drawing 4 and the accompanying drawing 8: afterburning lever combination part is positioned on the large support 4 by pivot pin 5.
Shown in Figure of description 2 and the Figure of description 8: two miniature bearings 7 are assemblied on the power end and afterburning end of afterburning lever 6 by two bearing pivot pins 8, and fix at the aperture riveted.
Shown in the Figure of description 2: the miniature bearing 7 that is installed in the reinforcing end of afterburning lever 6 directly is pressed on the afterburning ring 23 of lever along the direction of axis line of large support 4, plane bearing 1 is positioned on the afterburning ring 23 of lever with cylindrical, 25 one-tenth transition fit of the endoporus of plane bearing 1 and brake hoop connect, friction plate 27 end faces are fitted in brake hoop 25 and the friction plate assembly, and another friction plate 27 is fitted with the brake disc of driven coupling 28 in the friction plate assembly.
Shown in Figure of description 2 and the Figure of description 5: two friction disc supports 26 form with adopting the adhesive bonding connecting of two friction plates 27.
Shown in Figure of description 2 and the Figure of description 7: driven coupling 28 is positioned on the lower end cap 1 by plane bearing 2 29, rolling bearing 30 and shaft block ring B 31, and the brake disc on the driven coupling 28 directly contacts with friction plate 27 and produces friction.
Shown in Figure of description 2 and the Figure of description 3: initiatively coupling 14 and brake hoop 25 adopt the splines connection that is slidingly matched.
Shown in Figure of description 2 and the Figure of description 9: the A place promotes the braking conical surface that lever is used on the spring seat 18.
Shown in the Figure of description 10: the B place is in braking state for driven coupling brake disc and friction plate, and the C place is in braking state for brake hoop and friction plate.
Shown in the Figure of description 11: the D place is in disengaged condition for driven coupling brake disc and friction plate, and the E place is in disengaged condition for brake hoop and friction plate.
Shown in the Figure of description 14: the F place is work right hand helix face in the driven coupling, and the H place is the left-handed helicoid of work, and the G place employs the right hand helix face, and the J place employs left-handed helicoid.
Shown in the Figure of description 15: initiatively the O place is work right hand helix face in the coupling, and the Q place is the left-handed helicoid of work, and the P place employs the right hand helix face, and the R place employs left-handed helicoid
Shown in Figure of description 12 and the Figure of description 13: the difference of relative position relation was that the latter Duoed a size S than the former when relative position relation was shut down braking with brake hoop 25 and active coupling 14 when brake hoop 25 was with 14 work of active coupling in the thrust type braking load-limiting coupler; the former S is zero, i.e. assembling is finished the relative brake hoop of active coupling and also had vertically a displacement amount backward.
Shown in Figure of description 2 and the Figure of description 14: driven coupling 28 adopts bidentate face structure, and wherein internal layer flank of tooth helix angle is greater than outer flank of tooth helix angle.
Shown in Figure of description 2 and the Figure of description 15: initiatively coupling 14 adopts bidentate face structures, and wherein internal layer flank of tooth helix angle is greater than outer flank of tooth helix angle, and with driven coupling 28 internal and external layer flank of tooth helix angles coupling.
The working procedure of this bidentate face thrust type braking load-limiting coupler: power source is inputted from active coupling 14 splined holes, the engagement that internal layer starting helical tooth flank by active coupling 14 and the internal layer of driven coupling 28 start helical tooth flank has produced the end thrust greater than brake spring, brake off, after initiatively coupling 14 input torques are stablized or are continued to strengthen, initiatively coupling 14 and driven coupling 28 internal layers starting helicoid exchanges to outer working screw face, produce axial displacement compression brake springs 22 and reach balance with spring pressure in order to reach coupling 14 initiatively, at this moment initiatively coupling 14 drives brake hoop 25, the branched afterburning lever 6 of the afterburning ring 23 reverse promotions of plane bearing 1 and lever moves along the braking conical surface of spring seat 18, lay down simultaneously and add the braking force that is pressed on the friction plate 27, brake off, the effect of performance coupling is carried out transmission; When working machine transships, initiatively the axial force along axial direction also increases thereupon on the coupling 14, initiatively coupling 14 must produce displacement along axial direction, further compression brake spring 22 is in order to reach the balance with brake spring 22 thrusts, until initiatively the outer working screw flank of tooth of coupling 14 and the outer working screw flank of tooth of driven coupling 28 are thrown off fully, this moment, coupling was in the state that skids, machine has been protected in no longer transmission, has realized the limit for tonnage protection; Power source is removed; torque disappears; state before the pressure of the brake spring 22 that active coupling 14 axially is subject to also resets into shutdown thereupon; this moment, the energy of brake spring 22 savings discharged immediately; promoting initiatively, coupling 14 moves to driven coupling 28 directions; drive is positioned at spring seat 18 synchronizing movings on the active coupling 14; the braking conical surface on the spring seat 18 promotes to be installed in the miniature bearing 7 on the afterburning lever 6; drive afterburning lever 6 and pass to successively plane bearing 1 by another miniature bearing 7 pressurizations to the afterburning ring 23 of lever; brake hoop 25; friction plate 27; friction disc support 26; brake disc on friction plate 27 and the driven coupling 28; the brake disc that makes brake hoop 25 and driven coupling 28 respectively with friction plate 27 combinations; produce friction; the braking moment that formation has strengthened realizes braking.
Thrust type braking load-limiting coupler is reasonable in design, and compact structure is sensitive reliable, can be widely used in the multiclass mechanical transmission coupling.
Claims (6)
1. a bidentate face thrust type is braked load-limiting coupler, it is characterized in that: afterburning lever (6) is assemblied on the large support (4) by pivot pin (5), two miniature bearings (7) are assemblied on the power end and afterburning end of afterburning lever (6) by two bearing pivot pins (8) respectively, spring seat (18) is by shaft block ring A (15), rolling bearing (16) and hole are positioned on the active coupling (14) with back-up ring (21), branched brake spring (22) becomes to be arranged in parallel, one side pressure is lived spring seat (18), the other end withstands afterburning pivot pin (20), the miniature bearing (7) of the reinforcing end of afterburning lever (6) directly is pressed on the afterburning ring of lever (23) along the direction of axis line of large support (4), plane bearing one (24) is positioned on the afterburning ring of lever (23) with cylindrical, the endoporus of plane bearing one (24) becomes transition fit to connect with brake hoop (25), friction plate (27) end face is fitted in brake hoop (25) and the friction plate assembly, and another friction plate (27) is fitted with the brake disc of driven coupling (28) in the friction plate assembly.
2. according to claim (1) bidentate face thrust type braking load-limiting coupler, driven coupling (28) adopts the double-layer spiral cutting structure, and initiatively coupling (14) adopts the double-layer spiral cutting structure.
3. according to the described bidentate face of claim (1) thrust type braking load-limiting coupler, internal layer flank of tooth helix angle is greater than outer flank of tooth helix angle in the driven coupling (28), and initiatively the middle internal layer flank of tooth helix angle of coupling (14) is greater than outer flank of tooth helix angle.
4. according to the bidentate face thrust type braking load-limiting coupler of claim (1), driven coupling (28) and active coupling (14) internal and external layer flank of tooth helix angle are complementary.
5. according to the described bidentate face of claim (1) thrust type braking load-limiting coupler, there is a place to promote the braking conical surface that lever is used on the spring seat (18).
6. according to the described bidentate face of claim (1) thrust type braking load-limiting coupler, initiatively coupling (14) and brake hoop (25) adopt spline connections that be slidingly matched, initiatively the relative brake hoop (25) of coupling (14) displacement amount backward in addition vertically.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210070707.0A CN103307156B (en) | 2012-03-15 | 2012-03-15 | Bidentate face thrust type braking load-limiting coupler |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210070707.0A CN103307156B (en) | 2012-03-15 | 2012-03-15 | Bidentate face thrust type braking load-limiting coupler |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103307156A true CN103307156A (en) | 2013-09-18 |
| CN103307156B CN103307156B (en) | 2015-11-25 |
Family
ID=49132725
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201210070707.0A Expired - Fee Related CN103307156B (en) | 2012-03-15 | 2012-03-15 | Bidentate face thrust type braking load-limiting coupler |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN103307156B (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105299110A (en) * | 2014-06-25 | 2016-02-03 | 湖北省咸宁三合机电制业有限责任公司 | Power-on de-braking load-limiting coupler |
| CN110815288A (en) * | 2018-08-09 | 2020-02-21 | 达明机器人股份有限公司 | Brake device of robot arm |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2001031219A1 (en) * | 1999-10-29 | 2001-05-03 | Curt Falk Ab | A torque-limiting coupling device |
| GB2370077A (en) * | 1997-08-01 | 2002-06-19 | British Autogard | Torque limiting clutch with manual disengagement means |
| CN1948777A (en) * | 2005-10-11 | 2007-04-18 | 小仓离合器有限公司 | Power transmission device |
| CN201050558Y (en) * | 2006-12-05 | 2008-04-23 | 湖北省咸宁三合机电制业有限责任公司 | Braking and load-limiting coupler |
| CN101813146A (en) * | 2009-02-20 | 2010-08-25 | 湖北省咸宁三合机电制业有限责任公司 | Coupling braking load limiter |
| CN202560899U (en) * | 2012-03-15 | 2012-11-28 | 湖北省咸宁三合机电制业有限责任公司 | Double tooth surface stressing type braking and load limiting coupler |
-
2012
- 2012-03-15 CN CN201210070707.0A patent/CN103307156B/en not_active Expired - Fee Related
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2370077A (en) * | 1997-08-01 | 2002-06-19 | British Autogard | Torque limiting clutch with manual disengagement means |
| WO2001031219A1 (en) * | 1999-10-29 | 2001-05-03 | Curt Falk Ab | A torque-limiting coupling device |
| CN1948777A (en) * | 2005-10-11 | 2007-04-18 | 小仓离合器有限公司 | Power transmission device |
| CN201050558Y (en) * | 2006-12-05 | 2008-04-23 | 湖北省咸宁三合机电制业有限责任公司 | Braking and load-limiting coupler |
| CN101813146A (en) * | 2009-02-20 | 2010-08-25 | 湖北省咸宁三合机电制业有限责任公司 | Coupling braking load limiter |
| CN202560899U (en) * | 2012-03-15 | 2012-11-28 | 湖北省咸宁三合机电制业有限责任公司 | Double tooth surface stressing type braking and load limiting coupler |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105299110A (en) * | 2014-06-25 | 2016-02-03 | 湖北省咸宁三合机电制业有限责任公司 | Power-on de-braking load-limiting coupler |
| CN110815288A (en) * | 2018-08-09 | 2020-02-21 | 达明机器人股份有限公司 | Brake device of robot arm |
| CN110815288B (en) * | 2018-08-09 | 2022-06-21 | 达明机器人股份有限公司 | Brake device of robot arm |
Also Published As
| Publication number | Publication date |
|---|---|
| CN103307156B (en) | 2015-11-25 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN210889832U (en) | Torque limiting clutch assembly | |
| CN103821928A (en) | Gear shift arrangement with parking block and method for its actuation | |
| CN101837938B (en) | Unidirectional load self-braking spiral braking device | |
| CN105485196A (en) | Torque limiter provided with gear friction plates | |
| CN104653647A (en) | Shock-absorption buffer shaft and application | |
| CN202560898U (en) | Boosting type braking load-limiting coupling | |
| CN202901080U (en) | Drum type gear connection structure | |
| CN202560899U (en) | Double tooth surface stressing type braking and load limiting coupler | |
| CN103307156A (en) | Double-toothed-surface forced braking and load-limitation coupling | |
| CN105065487B (en) | A kind of clutch of motorcycle | |
| CN202579768U (en) | Double-tooth-surface braking load limit coupler | |
| CN101813146A (en) | Coupling braking load limiter | |
| CN102758900A (en) | Hydrodynamic transmission used for hydrodynamic forklift and provided with pump mechanism | |
| CN103307155A (en) | Stressing-type brake load-limiting coupler | |
| CN102537270A (en) | Clutch type high-power efficient mechanical torque converter | |
| CN204647042U (en) | A kind of damping, buffering axle | |
| CN204878417U (en) | Motorcycle clutch | |
| KR101350229B1 (en) | Planetary gear type gear speed reducer | |
| CN208845598U (en) | Clutch and automobile with the clutch | |
| WO2020034540A1 (en) | Clutch and vehicle provided with same | |
| CN106907302B (en) | Bidirectional asymmetric slip torque limiter | |
| CN201368156Y (en) | Inertia tensioning clutch | |
| CN203516508U (en) | Limit moment coupler locking device | |
| CN203404297U (en) | Braking load-limiting coupler with forward and backward spiral sleeve | |
| JP4838511B2 (en) | Shaft coupling and gear transmission provided with the same |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20151125 Termination date: 20170315 |